EP0219667B1 - Dispositif d'injection de combustible pour moteurs diesel - Google Patents

Dispositif d'injection de combustible pour moteurs diesel Download PDF

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Publication number
EP0219667B1
EP0219667B1 EP19860112319 EP86112319A EP0219667B1 EP 0219667 B1 EP0219667 B1 EP 0219667B1 EP 19860112319 EP19860112319 EP 19860112319 EP 86112319 A EP86112319 A EP 86112319A EP 0219667 B1 EP0219667 B1 EP 0219667B1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel
pump
piston
leak
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP19860112319
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German (de)
English (en)
Other versions
EP0219667A1 (fr
Inventor
Peter Fuchs
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sulzer AG
Original Assignee
Gebrueder Sulzer AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gebrueder Sulzer AG filed Critical Gebrueder Sulzer AG
Publication of EP0219667A1 publication Critical patent/EP0219667A1/fr
Application granted granted Critical
Publication of EP0219667B1 publication Critical patent/EP0219667B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps peculiar thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/361—Valves being actuated mechanically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention relates to a fuel injection device for a diesel internal combustion engine, with a fuel pump which has a pump piston driven by a camshaft and delivers fuel into a pump chamber, with a suction valve which determines the start of delivery of the pump and an overflow valve which determines the delivery end of the pump.
  • the suction valve and the overflow valve are controlled as a function of the piston movement, the pumping phase of the pump beginning with the closing of the suction valve and the pumping phase of the pump ending with the opening of the overflow valve.
  • the pump delivers the fuel under high pressure via a pressure line to the injection valve in the cylinder.
  • the quantity of fuel injected into the cylinder via the injection valve during this delivery phase has the result that the pressure of the air compressed in the cylinder gradually increases after the start of injection up to an ignition pressure maximum value and then drops. This permissible maximum value of the ignition pressure determines the start of injection, which is usually after top dead center.
  • the invention has for its object to improve a fuel injection device of the type mentioned so that the described optimal ignition pressure curve is achieved in the cylinder.
  • the pump piston is provided with at least one control edge which is connected to the pump chamber and which cooperates with an opening in the cylinder wall of the pump, in that a fuel-filled chamber which is connected to this opening is provided in the pump , which is also connected to the outflow side of the overflow valve via a refill valve and a control valve, that a piston acted upon by this fuel is arranged in the fuel-filled space and interacts with the overflow valve in such a way that - when the delivery begins before top dead center - the overflow valve opens during the delivery phase, when the control edge connects the pump chamber to the fuel-filled chamber via the opening in the cylinder wall, and that the overflow valve is closed during the delivery phase by opening the control valve.
  • the amount of fuel otherwise injected into the cylinder in an uninterrupted phase - by briefly opening the overflow valve and thus briefly relieving pressure on the fuel in the pump chamber - is divided into two sections, the interval between these two sections depending on the point in time opening of the control valve can be changed.
  • the distribution of the total amount of fuel to be injected can be selected such that approximately 20% of the total amount of fuel is injected during the first section and accordingly about 80% during the second section.
  • the start of injection is brought forward compared to that of the known devices, namely before top dead center. This advance means that the maximum ignition pressure is shifted towards top dead center, whereas the reduced or interrupted delivery and injection keep this ignition pressure practically constant at the maximum value during most of the combustion process.
  • a bushing 50 with a cylinder bore 8 is provided in a pump housing 1, in which a pump piston 2 is sealingly guided.
  • the pump piston is provided at its lower end in FIG. 1 with a roller 3 which is pressed against a cam 5 of a camshaft 6 by a spring 4 supported on the housing 1.
  • a pump chamber 7 is formed in the pump housing 1 and communicates with the cylinder bore 8.
  • An inlet channel 10 opens into the pump chamber 7 and is provided with a suction valve 11 at its mouth into the chamber 7.
  • the suction valve 11 has a seat surface 12 provided in the pump housing and a valve body 13 which interacts with it and is pressed against the seat surface 12 by a spring 14.
  • the valve body 13 has a downwardly projecting pin 15, which cooperates with a plunger 16 guided in the housing 1.
  • the plunger 16 is pressed down by a spring 17 which is supported on the housing 1 and rests with its lower end in a recess in a two-armed control lever 18.
  • the control lever 18 lies with its central section on an eccentric pin 21 and is guided with its right end in FIG. 1 between two guide surfaces 20 on the pump piston 2.
  • the eccentric pin 21 is pivotally mounted in a manner not shown, whereby the timing of the closing of the suction valve 11 can be set.
  • a supply line 44 for diesel fuel opening into the inlet channel 10 is connected to the pump housing 1.
  • An output channel 43 is provided in the pump housing 1, which extends from the pump chamber 7 and opens at its upper end into a delivery line 45 connected to the housing 1, which leads to an injection valve (not shown) in the cylinder of the internal combustion engine.
  • the outlet channel 43 has a pressure valve 40 which consists of a seat 41 provided in the housing 1 and a valve body 42 which is pressed into the closed position by a spring 46.
  • An overflow channel 22 is provided in the pump housing 1, which also branches off from the pump chamber 7 and is provided with an overflow valve 24.
  • the overflow valve 24 consists of a seat 25 in the housing 1 and a valve body 26 which is pressed against the seat by a spring 27.
  • the valve body 26 has a downwardly projecting pin 28 which cooperates with a plunger 30 guided in the housing 1.
  • the tappet is pressed down by a spring 31 supported on the housing 1 and rests with its lower end in a recess in a control lever 32 which rests with its right end on an eccentric pin 33 and with its left end between the surfaces 20 of the pump piston 2 is led.
  • the eccentric pin 33 like the eccentric pin 21, is mounted in such a way that by pivoting the pin, the point in time at which the overflow valve 24 opens and thus the end of the delivery phase can be changed.
  • the bushing 50 With its upper flange in FIG. 1, is let into a corresponding recess in the pump housing 1 and is surrounded below the flange by a ring 51, which is likewise accommodated in a corresponding recess in the housing 1.
  • the ring 51 and thus also the bushing 50 are fastened in the pump housing 1 by means of a plurality of screws distributed over the circumference of the ring 51, one of which is indicated by the dash-dotted line 52 in FIG. 1.
  • In the socket 50 are distributed over its circumference and at the same height several openings 38 are provided, which open into an annular cavity of the ring 51, which is connected via a bore 53 in the ring 51 to a space 70 in which a piston 71 is arranged is.
  • the piston 71 is attached to the plunger 30, and the top of this piston also serves as an abutment for the spring 31.
  • a bore 39 leads from the space 70 to the overflow channel 22, a spring-loaded refill valve 60 being arranged in this bore. This refill valve ensures that the bore 39, the space 70 and the bore 53 cannot be sucked empty during the delivery stroke of the pump piston 2, since fuel can flow in from the overflow channel 22 via the refill valve 60 if a vacuum is created in this volume. This volume is therefore always filled with fuel, this fuel being at a slightly lower pressure than the fuel in the channel 22.
  • a bore 47 branches off from the refill valve 60 and also opens into the overflow channel 22 via a control valve 48.
  • the control valve 48 of which only the closure part is shown in FIG. 1, can be actuated electrically, hydraulically or also mechanically.
  • the pump piston 2 has a channel 37 which extends transversely to its longitudinal axis and over part of its circumference, the upper boundary of which in FIG. 1 forms a control edge 36 which interacts with the openings 38 in the cylinder sleeve 50.
  • the channel 37 is connected to the pump chamber 7 via an axial channel 34 which is arranged in the outer surface of the piston 2.
  • the control edge 36 extends somewhat obliquely to the longitudinal axis of the pump piston 2, which is separated from its lower part 2 'above the upper guide surface 20.
  • the upper part of the pump piston 2 has a flange 54, which is provided with a radial projection 55, to which a linkage, not shown, is connected. With the aid of this linkage, the upper part of the pump piston 2 can be rotated somewhat about its longitudinal axis, so that the position of the control edge 36 relative to the openings 38 can be changed.
  • the pump piston 2, 2a is moved upward by the cam 5 in FIG. 1, the suction valve 11 initially being in the open position because the control lever 18 still presses the tappet 16 against the pin 15.
  • the pressure valve 40 and the overflow valve 24 are still closed.
  • the suction valve 11 is closed, and the delivery phase and thus the injection process begins, in that the pump piston 2, 2a presses the fuel in the pump chamber 7 into the delivery line under high pressure 45 presses, the pressure valve 40 is open.
  • the start of the funding phase is labeled A in FIG. 2.
  • the interruption is ended by a corresponding Si gnal the control valve 48 is opened so that the high pressure in the space 70 below the piston 71 is reduced via the bores 39 and 47 and the piston 71 returns to the position shown in FIG. 1, in which the overflow valve 24 is closed.
  • This Schliesszeittician where al so the pumping phase will be continued via the pressure line 45 to the injection valve is indicated in Fig. 2 with C.
  • the delivery phase or injection is ended when the control lever 32 opens the overflow valve 24 via the plunger 30, which corresponds to point D in FIG. 2.
  • the pressure in the pump chamber 7 decreases via the overflow channel 22.
  • the overflow valve 24 is closed and the suction valve 11 is opened, with which new fuel enters the pump chamber 7.
  • the time interval between points B and C can be varied, in particular made very small.
  • the rotatable piston part 2 it becomes possible to shift the injection-free interval, i.e. the interruption time between points B and C in Fig. 2, towards point A or towards point D, e.g. depending on the load of the internal combustion engine.
  • a plurality of channels corresponding to the channel 37 can be provided on the pump piston 2 offset in the axial direction, each of which is connected to the pump chamber 7 via its own axial channel.
  • the piston has a sleeve which on the one hand slides on the plunger 30 and on the other hand in the pump housing 1 and whose upper end face abuts the pin 28 of the overflow valve 24 when the piston moves upward.
  • the spring 31 pressing the plunger 30 onto the control lever 32 is then arranged outside the pump housing, as is the case with the plunger 16 of the suction valve 11.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)

Claims (6)

1. Dispositif d'injection de carburant d'un moteur diesel à combustion interne, qui comporte une pompe (1) de carburant comprenant un piston (2, 2a) de pompe mû par un arbre (6) à cames et destiné à refouler du carburant dans une chambre (7) de pompe, et qui comporte une soupape (11) d'aspiration déterminant le début de refoulement de la pompe, ainsi qu'une soupape (24) de décharge déterminant la fin de refoulement de la pompe, caractérisé par le fait que le piston (2, 2a) de pompe est pourvu d'au moins un bord (36) de commande communiquant avec la chambre (7) de pompe et correspondant à une lumière (38) dans la paroi de la chemise, qui est ensuite caractérisé par le fait que la pompe contient une chambre (70) qui communique avec la lumière (38) et est remplie de carburant, et qui communique, de surcroît, par l'intermédiaire d'un clapet (60) de réalimén- tation et d'une soupape (48) de pilotage, avec la canalisation (22) de décharge de la soupape (24) de décharge, qui est ensuite caractérisé par le fait qu'un piston (71) est placé dans la chambre (70) remplie de carburant, ce piston étant soumis à l'action de la pression du carburant et lié au fonctionnement de la soupape (24) de décharge, de telle sorte que - lorsque le début de refoulement se situe avant le point mort haut - la soupape (24) de décharge s'ouvre pendant la phase de refoulement lorsque le bord (36) de commande découvre, au travers de la lumière (38) dans la paroi de la chemise, la communication entre la chambre (7) de pompe et la chambre (70) remplie de carburant, et caractérisé enfin par le fait que la soupape (24) de décharge est refermée, lors de la phase de refoulement, par l'ouverture de la soupape (48) de pilotage.
2. Dispositif d'injection de carburant selon la revendication 1, caractérisé par le fait qu'une tringle (30) reposant sur un culbuteur (32) est prévue, qui est destinée à actionner la soupape (24) de décharge à la fin de la phase de refoulement, et caractérisé par le fait que le piston (71) logé dans la chambre (70) remplie de carburant est relié à la tringle (30).
3. Dispositif d'injection de carburant selon la revendication 2, caractérisé par le fait qu'un ressort (31), plaquant la tringle (30) contre le culbuteur (32), s'appuie sur le piston (71).
4. Dispositif d'injection de carburant selon l'une des revendications 1 à 3, caractérisé par le fait que le tronc du piston (2, 2a) de pompe comportant le bord (36) de commande est réalisé de façon à pouvoir pivoter autour de son axe longitudinal et relativement par rapport à la lumière (38) dans la paroi de la chemise.
5. Dispositif d'injection de carburant selon l'une des revendications 1 à 4, caractérisé par le fait que plusieurs bords de commande sont répartis sur la longueur du piston de pompe.
6. Dispositif d'injection de carburant selon l'une des revendications 1 à 5, caractérisé par le fait qu'un axe excentrique réglable (21) est prévu pour permettre la modification du point de fermeture de la soupape (11) d'aspiration.
EP19860112319 1985-10-18 1986-09-05 Dispositif d'injection de combustible pour moteurs diesel Expired EP0219667B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH449785A CH667900A5 (de) 1985-10-18 1985-10-18 Brennstoffeinspritzvorrichtung fuer eine dieselbrennkraftmaschine.
CH4497/85 1985-10-18

Publications (2)

Publication Number Publication Date
EP0219667A1 EP0219667A1 (fr) 1987-04-29
EP0219667B1 true EP0219667B1 (fr) 1989-01-25

Family

ID=4277208

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19860112319 Expired EP0219667B1 (fr) 1985-10-18 1986-09-05 Dispositif d'injection de combustible pour moteurs diesel

Country Status (4)

Country Link
EP (1) EP0219667B1 (fr)
JP (1) JPS6299670A (fr)
CH (1) CH667900A5 (fr)
DK (1) DK159079C (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH670866A5 (fr) * 1986-09-17 1989-07-14 Sulzer Ag

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH148854A (de) * 1929-11-13 1931-08-15 Sulzer Ag Brennkraftmaschine mit Selbstzündung und unterteilter Einspritzung der für einen Arbeitsvorgang in einem Arbeitsraum bestimmten Brennstoffmenge.
FR2554173B3 (fr) * 1983-10-27 1986-02-21 Renault Dispositif d'injection pilote pour moteurs a combustion interne
DE3541049A1 (de) * 1984-11-23 1986-06-05 AVL Gesellschaft für Verbrennungskraftmaschinen und Messtechnik mbH, Prof. Dr.Dr.h.c. Hans List, Graz Einrichtung zur unterbrechung des druckaufbaues bei einer kraftstoffeinspritzpumpe

Also Published As

Publication number Publication date
CH667900A5 (de) 1988-11-15
DK363286D0 (da) 1986-07-30
JPS6299670A (ja) 1987-05-09
DK159079B (da) 1990-08-27
DK159079C (da) 1991-02-04
DK363286A (da) 1987-04-19
EP0219667A1 (fr) 1987-04-29

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